Automatically-adjusting speed or revolution change gear.



G. S. MORISON.

AUTOMATICALLY ADJUSTING SPEED 0R REVOLUTION CHANGE GEAR.

APPLICATION FILED NOV.23, 1918. '1,Q91,654.

Patented Jan. 14, 1919.

lvbv eni'br.

6' 5. Morr ism.

iii y a ITED era nr ornrcn.

GEORGE SMITH MORISON, OF MELBOURNE, VICTORIA, AUSTRALIA.

AUTOMATICALLY-ADJUSTING SPEED 0R REVOLUTION CHANGE GEAR:

Specification of Letters Patent.

Patented J an. 14, 1919.

Application filed November 23, 1918. Serial No. 268,915.

To all whom it may concern:

Be it known that I, GEORGE SMITH Monr- SON, a subject of the King ofGreat Britain, residing at Collins House, 360 Collins street, Melbourne,in the State of Victoria, Australia, have invented certain new anduseful Improvements in Automatically-Ad usting Speed or RevolutionChange Gear; and I do declare the following to be a full, clear, andexact description of the invention, such as will enable others skilledin the art to which it appertains -to make and use the same.

This invention relates to a device for reducing or increasing the speed,or number of revolutions, of any revolving portion of a machine orgearing, such as any pulley, shafting, reel, drum, machine, or anyportion of a machine, which is being driven through the agency of ahigher or lower speed prime mover or shafting.

For the purpose of explanation I have shown in this specification andaccompanying drawings one form of application of my invention to achievethe increase or decrease of speed for general purposes, but I would haveit understood that the matter therein shown may be applied, in modifiedforms, to suit varying requirements without departing from the nature ofmy invention.

In order that my invention may be the more easily understood referencemay be made to the accompanying drawings in which Figure 1 is a frontelevation of apparatus embodying my invention.

Fig. 2 is a similar view, but with the front standard frame or casingremoved.

Fig. 3 is a side elevation parts of which are in section.

Fig. 4 is a cross section showing the position of rollers and linksduring certain functions of the gear as will be hereinafter ex lained.

ig. 5 shows a side view of the links with the upper and lower rollers orwheels respectively in place.

Fig. 6 is a detail showing the central shaft with collars thereon.

Fig. 7 is also a detail showing the top rollers and spindle thereof andFig. 8 shows the outer ring or rim in section showing the annular trackor groove in which the rollers or wheels operate while Fig. 9illustrates how the links hereinafter to be referred to may beconstructed to operate with the rollers in a slightly differentposition.

In these drawings a is a central collar, roller, pulley or boss, fixedon or forming part of the high-speed or driving shaft a of the primemover. Around this central collar 0 on the shaft a are placed three ormore circular rollers, disks, or pulleys b, situated at approximatelyequal distances from each other or in any predetermined po sition. Eachroller brevolves on its own axis or central pin, and is in contact with,and rolls between, the central collar a on shaft and an outer ring orrim 0 that encircles the rollers Z). One or more or all the rollers bmay be fitted in suitable fixed or adjustable bearings as at b, orlinked together as may be determined, by links (I.

The links (1 are automatically adjustable .in accordance with the pullof the central collar a by running top rollers b or I may, however,employ in lieu of the top rollers 6 two fixed lateral rollers e actingas limitation stoppers against undue distance between the said links 03(see Fig. 9).

The rollers b are placed in the annular space f between the collar 0. onthe high speed shaft a and the inside face 0 of the outer ring 0, andare differential in size, reducing or varying in diameters in at fixedor predetermined ratio from the diameter of the larger top roller 6 tothat of the smallest or bottom rollers 12 in the train. This has theeffect of placing the geometrical center of the outer ring 0 eccentricto that ofthe central or high speed shaft a the amount of eccentricityof the centers being determined by the difference in diameters of therollers and their positions when placed in the annular space between theshaft (1. and outer ring a.

The fixed collar (1 on shaft a, also the rollers b, and the inside face0' of ring 0 are all turned true circles with true arallel faces, butsame may be all turned with circular grooved faces, the convex faces ofeach part to fit into the concave grooved faces of the other part andthereby securing increased gripping contact.

The speed or number of revolutions of the outer ring a will beproportionately lower than that of the central or high speed drivingshaft a according to the ratio of the diameter of the inside of the ringa to that of the fixed collar (1 on the shaft 0., and the Q vmemesdiameters of the rollers b, and b these diameter ratios to bepredetermined for a given speed reduction.

The rollers b and b may be stepped, or turned with two diameters, sothat the larger diameter of each roller would be in contact with, andrevolve on, the central collar a on the shaft 01/, and the smallerdiameter of each roller would be in contact with and carry or supportthe outside ring 0, thus causing a two-speed-change or a secondreduction of speed or revolutions and conse quently much greaterreduction in revolutions of the outer ring 0.

The outside ring 0 at its comparatively lower speed may be used in itsposition on the high speed shaft either as a pulley for belt drivingother machinery, or used for coupling to and driving another length ofshafting at the reduced speed, or with teeth cut on outside of ring 0may be used to mesh with or drive other gearing.

In operation, the rollers 6 being placed in an eccentric annular space 7between the driving shaft a and the outside ring 0, have a tendency towedge themselves tight, in rolling toward the narrowest or lower part ofthe said annular space f, and are therefore in continual contact withboth the collar to on the shaft 0- and the inside face 0 of outer ring0.

The largest roller or rollers b being placed approximately in the toppart of this annular space f between top side of shaft a and ring 0,leaves a smaller space at the bottom between underneath side of shaft aand bottom'of ring 0, this reduction in the space being gradual from theposition of the largest or top roller 6 at its points of contact withcollar a on shaft and outer ring 0 and continuing in its convergence tothe other or lower side of annular space f, diametrically opposite.

The rollers 72 therefore, according to their diameters take up theirrespective positions in the space 7 allowed by the decreasing orconverging environment, all rollers being thus in continual contact atall times with both the shaft at a and the inside face 0' of outer ring0 and exerting a pressure on both the shaft and the ring proportionateto the load or work demanded on the outer ring or pulley c. The shaft aduring work is therefore in compression, and the outer ring 0 intension.

Should wear take place on either the collar a on shaft (1, or on therollers b or 6 or on inside face of outer ring 0, the rollersautomatically take up a continuous gripping position further into theconverging annular space 7, all rolling faces being continuously inworking contact and wearing to fit.

In. the arrangement of the links as shown in Fig. 9 it will be seen thatthe top rollers 19 are dispensed with and their function effected by thetwo limitation lateral rollers c, the links being suitably shaped as atd to engage with the said lateral rollers e. It is obvious that if theshaft a be driven at a high speed the ring 0 will be reduced to a slowspeed, or if the latter be the source of movement, by a belt or otherconnection to the motor, the spindle of a will be acceleratedproportionately and thus the mechanism may be employed in general foreither speed reduction or acceleration as may be desired for each localfunction.

Since there are no sliding surfaces, and

all the contacts are on rolling surfaces, friction is at a minimum.

The operation may be reversed to produce high speed from low speed;

I claim:

1. In a change speed gearing, a rotatable shaft, a ring surrounding andeccentrically arranged relative to said shaft, rolling mernbers arrangedbetween and engaging said shaft and ring, and a rolling member havingits axis arranged stationary relative to said shaft and bearing upon theaxes of certain of the otherrolling members.

2. A change speed gearing comprisinga,

trically relatively to said shaft, a series of rolling members arrangedbetween and engaging said shaft and ring, axles movable with certain ofsaid rolling members, links connecting certain of said rolling members,and a rolling disk mounted between two of said rolling members andbearing upon said axles, said disk having its axis fixed relative to theaxis of the shaft.

In testimony whereof l have signed my name to this specification in thepresence of two subscribing witnesses.

GEORGE SMITH MORISON.

Witnesses:

DUKIE WINDRIDGE, Anens'rinn 'llrIoMAs MADDEN,

